Punching apparatus



1967 L. H. HASKIN, JR, ETAL. 3,296,910

PUNCHING APPARATUS Filed March 8, 1965 5 Sheets-Sheet 2 Jan. 10, 1967 L. H. HASKIN, JR, ETAL 3,296,910

PUNCHING APPARATUS Filed March 8, 1965 5 Sheets-Sheet 3 l I I40 I K w H 28 as \NVENTORS LAWRENCE H. HASK\N,JR. GEORGE W. KESLER 1967 L. H. HASKIN, JR., ETAL 3296,91

PUNCHING APPARATUS 5 Sheets-Sheet 4 Filed March 8, 1965 LAWRENCE H. HASKlN lR GEORGE W. KESLER BY J An g ATTORNEY Jan. 19, 1967 L. H. HASKIN, JR., ETAL 3,

PUNCHING APPARATUS 5 Sheets-$heet 5 Filed March 8, 1965 w: E a A INVENTORS LAWRENCE H. HASKINJR GEORGE W. KESLER ATTORNEYS United States Patent 3,296,910 PUNHTNG APPARATUS Lawrence H. Haslrin, In, and George W. Kesler, Richmend, Va., assignors to The llnta-Roto Machine Com-- pany, Tue, Richmond, Va., a corporation of Virginia Filed Mar. 8, 1965, Ser. No. 437,902 18 Claims. (Cl. 83-328) This invention relates to punching apparatus for forming longitudinally spaced apertures in a web or sheet, and more particularly to such apparatus capable of punching a plurality of rows of such apertures spaced transversely of a continuously traveling web.

In the formation of a plurality of rows or series of longitudinally spaced apertures in sheet or web stock having large width dimensions, many types of perforating or punching devices have been proposed in the prior art. One example of the known devices is the reciprocatory punch and die apparatus of the type wherein cooperating elements on opposite sides of the work are displaced toward each other to effect a punching operation and are then subsequently retracted. In the use of this device, the web being punched must be stopped for each punching operation.

Another type of device comprises a rotary apparatus wherein parallel cylinders having cooperating peripherally mounted punch and dies means are arranged on opposite sides of the web. Although the web can be moved continuously with this apparatus, the punches and dies must be oriented during each operation by springs and/or cams so as to be accurately aligned during the punching operations. Consequently, both production and maintenance of this type of apparatus is expensive.

Another example of known punching apparatus is of the link type wherein the punch and the die are respectively carried by a link the ends of which are mounted on cranks. This apparatus has the advantage of relatively high-speed operation on a continuously moving web, but for multiple row punching the punches and dies are carried by link supported platens which extend the full width of the web and the weight of the platens creates counterbalancing and maintenance problems.

In view of the difficulties involved with the prior art punching apparatus, industry has frequently found it desirable to avoid punching a continuous web, but instead to cut the web into sections of a given size for the particular use and then effect any punching that is necessary. For example, in the cigarette packaging industry, the outer paper wrapper must have the corners thereof beveled for use in the automatic folding machines. Consequently, it has been the practice to cut the sheet material into the necessary size, for example, about 6% x 4", to stack the out sheets and then to trim the corners and notch the centers of the longer sides. Obviously, this involves extra operations, and requires careful stacking for uniform trimming.

Having in mind the difiiculties of the prior art apparatus, it is the primary object of the present invention to provide a punching apparatus capable of producing a plurality of series or rows of spaced holes with the series being spaced transversely of a continuously moving web at a relatively high speed.

It is another object of the invention to provide a punching apparatus of the foregoing type that is dynamically balanced and has an extended useful life.

It is a further object of the invention to provide a punching apparatus having ease of assembly and capable of ready replacement and repair of worn parts.

It is a still further object of the invention to provide a punching apparatus incorporating the foregoing characteristics and having simplicity of design, economy of construction and efficiency in operation.

Briefly, according to the present invention, a highspeed punching apparatus includes a plurality of laterally-spaced parallel punch and die links arranged on 0pposite sides of a continuously traveling work sheet, and a plurality of parallel crankshaft means connected with the ends of said links for displacing the same toward and away from each other in timed relation relative to the rate of feed of the work. The apparatus is of relatively inexpensive, durable construction including a rigid frame made up of an assembly of a plurality of interconnected identical cast sections, each section being designed to rotatably support one of the crankshaft means at longitudinally spaced intervals, whereby relatively long crankshaft means may be utilized to accurately position and operate a plurality of die and punch links for forming apertures in sheets or webs having unusually large width dimensions.

Each crankshaft means includes an assembly of a plurality of counterbalanced eccentric and center shaft units that are so designed as to cause the total loads of the eccentrically connected links to be balanced along the length of, and relative to the axis of rotation of, the crankshaft means. At each end, each link is journaled on the center portion of a pin the ends of which are clamped in peripheral recesses contained in cylindrical body members with the pins eccentrically displaced symmetrically about the axis of rotation of the center shaft portions thereof. counterbalance weight members are secured to the body members diametrically opposite the pin means to further equalize the eccentric loading of the crankshaft means.

Each of the identical cast frame sections is so constructed that the eccentric and center shaft units are supported in the frame section by spaced ball bearing means arranged between each successive pair of cooperating punch and die links. As a consequence of the support of the rotary crankshaft means at spaced intervals along its length, as well as of the aforementioned angular distribution of the points of eccentricity relative to the axis of crankshaft rotation together with the counterbalancing means, extremely accurate punching of apertures in sheets having unusually large width dimensions and a relatively high rate of feed may be accomplished in an efficient, vibration-free manner.

The novel features that are considered characteristic of the invention are set forth with particularity in the appended claims. The invention itself, however, both as to its organization and its method of operation, together with additional objects and advantages thereof, will best be understood from the following description of a specific embodiment when read in connection with the accompanying drawings, wherein like reference characters indicate like parts throughout the several figures and in which:

FIG. 1 is a view in perspective of a punching apparatus in accordance with the present invention;

FIG. 2 is an enlarged cross-sectional view taken on line 22 of FIG. 1;

FIG. 3 is a cross-sectional view taken on line 33 of FIG. '2;

FIG. 4 is an exploded end view in elevation of the frame assembly of the apparatus;

FIGS. 5 and 6 are diagrammatic views corresponding with sectional views taken along lines 55 and 6-6, respectively, of FIG. 2;

FIG. 7 is an enlarged exploded view in perspective of a center eccentric shaft unit;

FIG. 8 is an enlarged perspective view of a eccentric shaft unit;

FIG. 9 is an enlarged, fragmentary, cross-sectional view showing the center section of FIG. 2 with the eccentric units =at least partially in cross section; and

FIG. is an enlarged cross-sectional view taken through a punch and die unit in a plane parallel to and generally encompassed by the phantom ova-l 10 in FIG. 3.

Referring first more particularly to FIG. 1, the punching apparatus of the present invention is operable to punch a plurality of series or rows of holes H in a longitudinally traveling sheet or web W of material, such as paper, a synthetic plastic, metal or the like. In the illustrated embodiment, the apparatus forms six transversely spaced, longitudinally extending series A, B, C, D, E and F, respectively of spaced holes H.

The apparatus includes a rigid frame 12 in which are journaled four crankshaft means 14 which may be individually identified 14a, 14b, 14c and 14:1. The crankshaft means 14 are disposed on parallel axes arranged rectangularly, and a plurality of parallel punch links 16, FIG. 3, are connected between the crankshaft means 14a and 1412 while a plurality of cooperative parallel die links 18 are connected between the crankshaft means 140 and Md. The links 16 and 18 are uniformly displaced angularly about their crankshaft means transversely of the apparatus to balance each other.

For convenience of fabrication and assembly, as best shown in FIGS. 1 and 4, the frame 12 of the apparatus may comprise four identical castings 12', one for each crankshaft means 14, which are assembled and secured together by bolts 20. Each of the castings 12' comprises flanged rectangular end panels 22 having a pair of holes 24 in each of at least two of their flanges 26 to accommodate the bolts 20. The panels 22 of each section are connected by a channel portion 28 which is braced by crosswebs 30 and has a plurality of bearing supports or hangers 32 extending from the bight portion of the channel 28 parallel with the end panels 22. Spacers may be inserted between the castings 12' to accommodate links of greater length and/ or throw circles.

The channel portion 28 is centrally disposed adjacent one side of each section 12' and the bearing supports 32 extend substantdiall-y to the opposite side of the section. Each section 12' is provided with a through bearing passage for the crankshaft means 14 and including like bearing openings 34 in the end panels 22 and openings 34' in the supports 32, and a second through passage aligned with said channel portion 28 and including bearing openings 36 in the end panels 22 and openings 38 in the crosswebs 30.

As best shown in FIG. 2, the crankshaft means 14 are uniformly and simultaneously driven from a power source S through a countershaft 40 including a gear 42 at one end and meshing with a gear 44 fixed to a lower crankshaft means, 14d for example, which in turn meshes with a gear 46 fixed with an upper crankshaft means, 14!) for example. The countershaft 40 extends through the web openings 38 in a lower section 12, parallel with the axes of the crankshaft means 14, is journaled by bearings 48 in the end panel openings 36 and has a gear 42' secured at its opposite end and which meshes with a gear 44 secured to the opposite end of the lower crankshaft means, and which meshes with a further gear 46 secured to the opposite end of the upper crankshaft means.

Driving the crankshaft means 14 at both ends precludes possible distortion due to torque. It has been found that if the links 16 and 18 are relatively displaced less than 180 it is necessary to drive only one set of the vertically displaced crankshaft means, such as 14d and 14b, the other two crankshaft means, such as 140 and 14a, being driven therefrom through the links 18 and 16, respectively. However, if the links are displaced 180", it is preferred to driveall four crankshaft means, as shown in FIG. 1, in which case there may be provided a second countershaft 40 and gear trains therefrom to the corresponding crankshaft means, as previously described. In this event, the power source S may comprise a gear meshing with the gears 42 on both countershafts.

The axes of countershaft or shafts 40 and the four crankshaft means are parallel and normal to the longitudinal direction of travel of the sheet W. Gears 44, 44' and 46, 46' have the same diameters, respectively, whereby the four crankshaft means 14 are driven at the same rotational speeds. In order that equal driving forces are applied to the ends of the crankshaft means, the power source S may be applied to both of the gears 42, 42' on opposite ends of the countershaft, if desired, as shown in FIG. 2. The gears 46, 46 are shown as split gears, portions of which may be selectively registered for antibacklash purposes.

As shown in FIG. 3, each of the upper links 16 contains in its lower surface a recess 50 in which'is secured, by downwardly extending screws 52, a punch block 54 that in turn carries one or more downwardly extending longitudinally spaced punch elements 56. Similarly, each of the lower links 18 has in its upper surface a recess 58 in which is secured, by downwardly depending screws 60, a die block 62 containing one or more die openings 64, FIG. 10, arranged to receive the respective punch element 56. The cross-sectional configurations of the die openings correspond with the cross-sectional configurations of the respective punch elements. Owing to the downwardly extending orientation of the screws 52 and 60, loosening and dropping out of the screws is prevented.

Referring to FIG. 10, each die opening 64 communicates at its lower end with an enlarged passage 66 which in turn communicates with a vertical through passage 68 in the lower link 18. These passages afford means for the removal by gravity of the portions of material severed from the sheet W by the punch and die means. The punch elements 56 are each slidably mounted in a recess 70 opening through the lower surface of the punch block 54. The punch elements 56 each have a threaded stud 72 on its upper end and which extends upwardly through a bore 74 into a recess 76 opening through the upper surface of the punch block for securement by a nut 78 within the recess 76. As the punch elements become worn and are resharpened, they may be properly repositioned by the interpositioning of one or more shims 80 between ehe upper end of the punch element and the top wall of the recess 70.

Each of the crankshaft means 14 is identical and consists of an assembly of center and eccentric shaft units that carry pins upon which the ends of the links are journaled. Referring more particularly to FIGS. 2 and 9, each crankshaft means 14 includes a center crankshaft unit 82 between the central pair of links 16 or 18, eccentric crankshaft units 84 and 84' arranged on opposite sides of the center crankshaft unit 82 and with links therebetween, and a pair of end crankshaft units 86 at the ends of the assembly. The only difference between the upper and lower crankshaft means 14 is their respective orientation to enable cooperative punch and die links to mate at the plane of the web W.

Each of the crankshaft units 82, 84, 84' and 86 include a hearing or shaft portion 88 and a crank or eccentric portion 90 on at least one side of the bearing portion 88 and separated therefrom by a threaded portion 92. The end crankshaft units 86 have only one crank portion 90, whereas the other crankshaft units 82, 84 and 84 each have two crank portions 90, one on each side of the shaft portion 88.

As best shown in FIGS. 79, each crank portion 90 comprises a generally cylindrical body 94 whose periphery is interrupted by a chordal surface 96 through which opens a semicylindrical recess 98. Internally threaded blind bores 100 open through the chordal surface on opposite sides of the recess 98. An arcuate clamp 102 having a semicylindrical inner surface 104 with diametrical end surfaces 106 and through bores 108 on each side thereof is secured on the chordal surface 96 by cap screws 110 extending through the through bores 108 and threaded into the blind bores 100.

The inner surface 104 of the clamp 102 and the recess 98 jointly form a cylindrical recess for receiving one end of a link pin 112. The axes of the cylindrical recesses formed by all of the crank portions 90 and clamps 102 are spaced an equal radial distance from the axes of the respective bearing portions 83. The only difference between the center crankshaft unit 82 and the eccentric crankshaft units 84-, 84 is that the recesses 93 in the two crank portions 90 of the center unit 82 are coaxial, as shown in FIG. 7, whereas the axes of the recesses 98 in the two crank portions 90 of the eccentric units 84, 84' are angularly displaced, as shown in FIG. 8.

Each of the crank portions 90 is provided with a radially disposed, internally threaded blind bore 114 diametrically opposite the semicylindrical recess 98 and an arcuate weight 116, having a centrally disposed through bore 118, is secured on the periphery of the cylindrical body 94 of the crank portion by a cap screw 120 extending through the bore 118 and threaded into the blind bore 114. The weight 116 counterbalances the weight of the clamp 102 and the link pin 112. It will be noted that the radius of the cylindrical body 94 is slightly less than that of the adjacent threaded portion 92, the radius of which, in turn, is slightly less than that of the bearing portion 88.

As shown in FIG. 2, the end crank units 86 are mounted in the openings 34 in the frame end panels 22, whereas the center and eccentric crank units 82, 8d, 84 are mounted in the openings 34' of the bearing supports 32. As more clearly shown in FIG. 9, the bearing portions 88 of the crank units are rotatably mounted in the openings 34, 34' by antifriction bearings 122 which comprise, preferably, dual ball bearing assemblies. The outer races of the bearings 122 are retained in the openings 34, 34' by retaining rings 124 which are secured to the end panels 22 and supports 32 by screws 126, whereas the inner bearing races are retained on the bearing portions 88 by ring nuts 128 threaded on the portions 92. The bearings for the end units 86 are somewhat wider than those of the intermediate crank units.

In assembly, the crank portions 90 of adjacent crank units are spaced to accommodate a crankpin 112 and a link 16 or 18 therebetween. The crankpins 112 have their ends respectively secured in the cylindrical recesses of the crank portions 90 by the clamps 102, best shown in FIG. 9. The crankpins 112 are provided centrally thereof with a pair of circumferential grooves 130 constituting raceways for ball bearings 132 which are retained by outer raceway means 134 fitted within openings in the ends of the links and secured by retainer rings 136 attached to the links by screws 138.

The cylindrical recesses in the crank portions 90 of the eccentric crank units 84, 84' are angularly displaced so as to balance the crankshaft means 14 as a Whole. The illustrated embodiment is adapted to punch six series or rows A through F of holes H so that the recesses and pins 112 are displaced 120. It will be understood, however, that for other embodiments adapted for punching a different number of rows of holes, the angular eccentricity may be such as to enable complete counterbalance of the number of links involved, and may be spaced, for example, 90, 180 or any other angle that will effect the desired result.

In the present instance, wherein the apparatus is adapted to punch six rows of holes, the crankshaft means 14 could be inherently balanced by displacing the link pins 112 through angles of 60". However, it is preferable that the crankshaft means 14 be dynamically balanced and, for this purpose, the crank units and links are arranged symmetrically from the center of the machine toward the ends of the crankshaft means 14. This arrangement may best be seen in FIG. 2 wherein the links 16 and 18 are specifically identified a through 7 to correspond to the rows A through F of holes to be punched.

It will be seen that the links are phased in pairs with said pairs displaced 120. That is, center links 0 and d are in phase and disposed, in FIG. 2, in central position at the web W, as shown in FIG. 3, whereas intermediate links b and e are in phase and displaced 120 forwardly, as shown in FIG. 5, and end links a and f are in phase and displaced 120 rearwardly, as shown in FIG. 6. To accomplish the symmetrical phasing of the links in pairs, the intermediate crank units 84 and 84 differ only in that their recesses 98 are displaced in relatively opposite directions in order to achieve the symmetrical displacement in pairs that results in dynamic balancing.

To maintain dynamic balance, it may be necessary to incorporate dummy links in addition to operative punch and die links. For example, to punch from two to four rows of holes, there must be two pairs of links phased 180. Thus, there would be one or two dummy links for this operation. Similarly, six links, as shown herein, in pairs phased 120 may be used for punching 5 or 6 rows, eight links in pairs phased or 180 may be used for punching 7 or 8 rows and twelve links in pairs phased 60 or for 9 to 12 rows, and the like.

In the illustrated machine, the punch blocks 54 accommodate three punch elements 56, as shown in FIG. 3, and the die blocks 62 have a like number of dies mating with said punch elements. The links 16 and 18 have a throw circle of twelve inches to accommodate a movement of twelve inches by the web Vi/ during each revolution, and the punch elements are spaced four inches apart so that the holes H in each row A through F are uniformly spaced four inches apart. It has been found that this machine can be operated at a rate of six hundred punch strokes a minute with twelve inch web lengths without deleterious effect either on the web or the machine.

From the foregoing description, it will be apparent that apparatus according to the present invention can be assembled with considerable ease. The bearings 122 of the crankshaft units may be fitted in the openings 34, 34' and secured by the retainer rings 124 and screws 126. Then the crankshaft units 82, 84, 84' and 86 can be inserted within the bearings 122 until their shaft portions 88 are centered within the bearings and then secured by threading the ring nuts 128 on the threaded portions 92 of the crankshaft units.

One of the arcuate weights 116 may be attached to the crankshaft units prior to mounting if the ring nut 128 is pre-threaded on the adjoining threaded portion 92, but the mounting of at least a second of the weights 116 must be delayed until the units are mounted within the bearings 122 to enable insertion of the units within the bearings. The crankshaft units may be mounted in the individual frame sections 12' prior to assembly of the frame sections, or the two upper and two lower frame sections may respectively be secured together either integrally or by the bolts 20 through the bolt holes 24-.

When the two upper and two lower crankshaft units are respectively mounted the links 16 and 18, which may previously have been fitted with their respective punch blocks 54 and die blocks 52, may be fitted on the outer races 134 of the bearings 132 which have previously been mounted in the grooves of the link pins 112 and retained by the rings 136 and their screws 138. The crankshaft units may then be oriented so that their semi-cylindrical openings 98 can receive the respective ends of the respective link pins 112, whereupon the clamp caps 102 can be secured to retain the pins in position with 'respect to the crank portions 90.

When the complete punch link assemblies are secured in the upper half frame and the die assemblies are se cured in the lower half frame, the cooperating punch and die links are then oriented so that the respective punch elements 56 will mate with their respective dies 64 and the two half frames may be secured together as by means of the bolts 20 and bolt holes 24, or they may be hingedly connected at one end and releasably clamped at the other end to facilitate separation for access to the punch elements 56 for sharpening purposes and the like.

Since the constructions of each of the four crankshaft means and their corresponding frame sections are identical, it is believed that further description of these parts is unnecessary. It should be mentioned that since the upper pinion gear or gears 46, 46' are driven by the lower pinion gear or gears 44, 44, respectively, the upper two frame sections 12' need not be provided with counter drive shaft means corresponding with the shaft or shafts 40 of the lower frame sections.

As shown in FIG. 4, the removal of one or more cast sections 12' from the frame is achieved merely by unfastening the connecting means. Owing to the vertical openings between the transverse brace portions 28 of the sections, as shown in FIG. 1, free access to the links from above or below the frame is permitted. The vari-- ous punch and die blocks 54 and 62, respectively, may be readily removed from their respective links for servicing, adjustment or replacement.

The versatility of the apparatus is increased as a result of the fact that punch elements 56 of various shapes and sizes, and corresponding die blocks, may be readily substituted on the links when it is desired to alter the configurations of the apertures formed in the web W. Moreover, different punch configurations may be provided on the same or different punch blocks for forming desired aperture configurations in the sheet.

A further advantage of the use of crankshaft means consisting of a plurality of assembledcenter and eccentric shaft units is that, during assembly of the crankshaft means in their respective frame sections, the ball bearing units may be secured by screwmeans to the frame and the links, respectively, whereby the assembled components of the crankshaft means are rigidly supported against lateral play by the annular side plates. Furthermore, the separable components of the crankshaft means permit assembly within a plurality of spaced bearings means, whereby the crankshaft means are supported for rotation at a plurality of points along their lengths. The individual links eliminate the excess metal and weight of single platens extending across the width of the web W.

In operation, referring again to FIG. 1, it is apparent that, when the drive gear S drives the pinion gears 42, 44 and 46, the links 16 and 18 are displaced by the various crankshaft means 14 in unison. This movement of the crankshaft means is in timed relation relative to the longitudinal rate of travel of the web W in the direction illustrated by the arrow. During the punching operation, the corresponding upper punch links 16 and the lower die links 18 are alternately brought together to effect punching of the web W and are displaced apart as the punched out material falls by gravity from the lower links. During this vertical displacement of the upper and lower links by the crankshaft means, the links are maintained parallel with each other and with the web W, while the web is moved a distance to enable the leading punch element to again engage the web at a uniform distance from the hole previously punched by the trailing punch element.

From the foregoing description, it will be apparent that punching apparatus according to the present invention operates on a continuous web motion principle so that the web is not subject to intermittent motion as necessitated by other types of apparatus. Theweb is not in contact with all of the punches during one punching cycle at the same time. The number of dies across the web have a staggered arrangement which forms a selfbalancing system and, with the dies phased in pairs, the system is dynamically balanced. Therefore, the process is a smooth, continuous operation and the web is kept under constant control under all speeds. A six row punching apparatus, such as illustrated in the drawings, is operated at a rate of 600 strokes per minute with a twelve inch web length.

Because of the smooth, continuous travel of the web throughout the punching operation and of the self-balancing feature of the punch die motion, this apparatus is highly efficient in inline processes, such as printing, coating and laminating; and the web can be fed directly to slitters, sheeters, folders and like equipment for all other related operations in converting web material to a finished product. The apparatus is also most economically adaptable for operation as a self-contained unit for preprinted materials. The web can be maintained under positive constant tension for an electronic register of the printed matter during an entire continuous process from unwinding, automatic side registration, slitting and rewinding for packaging.

Although a certain specific embodiment of the invention has been shown and described, it is obvious that many modifications thereof are possible. The invention, therefore, is not to be restricted except insofar as is necessitated by the prior art and by the spirit of the appended claims.

What is claimed is:

1. Apparatus for forming a plurality of transversely spaced rows of longitudinally spaced apertures in a continuous longitudinally moving web of sheet material, comprising a frame having a planar web path therethrough, a plurality of laterally spaced punch and die means each including corresponding upper and lower links arranged longitudinally of, parallel with, and on opposite sides of said web path, one of said links carrying at least one punch and the corresponding other of said links containing at least one die opening for receiving the punch, means for alternately displacing said links toward and away from each other including first and second pairs of parallel crank shaft means extending transversely of said web path on opposite sides thereof, 'respectively, and eccentric connections between the ends of the links and the respective pair of crank shaft means for displacing said upper and lower links toward and away from each other in orientations parallel with said web path to effect punching cooperation between the punches and the die openings carried thereby, said eccentric connections being angularly distributed relative to the axes of rotation of said crank shaft means to cause the resultant load of the links on each of the crank shaft means to be balanced.

2. Apparatus as defined in claim 1 wherein said upper and lower links are phased in pairs and arranged symmetrically from the center to the sides of the web path to dynamically balance said crank shaft means.

3. Apparatus as defined in claim 2 wherein said corresponding upper and lower links include at least one corresponding upper and lower pair of dummy links in excess of the number of rows of holes to maintain the dynamic balance.

4. Apparatus as defined in claim 1 wherein each of said crank shaft means comprises a plurality of crank shaft units each of which includes a cylindrical shaft portion and an eccentric portion on at least one side thereof and connected with one of said eccentric connections, and means on said frame journaling the shaft portion of each said shaft units on a common axis for each said crank shaft means.

5. Apparatus as defined in claim 4 wherein said crank shaft units are independently journalled in said frame and for each crank shaft means include two end units having only one eccentric portion on one side of the respective shaft portion, and at least one intermediate unit having an eccentric portion on each side of the respective shaft portion, said units being mounted with their respective eccentric portions in facing relation but spaced to accommodate a link therebetween, said ec- 9 centric connections comprising pins each supporting one end of a link and extending between two facing eccentric portions and thereby connecting all of the units of each crank shaft means.

6. Apparatus as defined in claim wherein the pair of pins connected to an intermediate unit have different angles of eccentricity relative to the axis of rotation of said crank shaft means.

7. Apparatus as defined in claim 6 wherein the pair of pins connected to at least one intermediate unit have the same angle of eccentricity relative to the axis of rotation of said crank shaft means.

8. Apparatus as defined in claim 5 wherein said eccentric portions of said units comprise a cylindrical body coaxial with and of a lesser diameter than the respective shaft portion, said body having a chordal surface thereon with a semi-cylindrical recess therein, and a semicylindrical cap removably secured on said surface and forming with said recess a socket for one end of one of said pins.

9. Apparatus as defined in claim 8 comprising counterbalance weight means removably mounted on said body diametrically opposite said pin socket.

10. Apparatus as defined in claim 9 wherein said frame comprises end portions'and a plurality of parallel transversely spaced bearing supports having axially aligned bearing openings for each said crank shaft means, anti-friction bearings in each said opening and including inner and outer races, rings removably mounted on said frame end portions and said bearing supports to secure 'said bearing outer races in said openings, the shaft portions of said crank shaft units being mounted within said inner bearing races respectively, said crank shaft units including threaded portions between the shaft portion and eccentric portions thereof and coaxial with said portions, said threaded portions having a diameter intermediate the diameters of said shaft and eccentric portions, and ring nuts threaded on said threaded portions to secure said shaft portions within the respective inner bearing races.

11. Apparatus as defined in claim 5 wherein said crank shaft means each include at least one intermediate unit wherein the pair of pins connected thereto have the same angle of eccentricity, and at least two intermediate units respectively on opposite sides of said one unit and wherein the pair of pins connected thereto have difiFerent angles of eccentricity which are identical but in relatively opposite directions, whereby the links carried thereby are phased in pairs.

12. Apparatus as defined in claim 1 wherein said frame comprises separable upper and lower sections, said first and second pairs of crank shaft means being journalled respectively in said upper and lower frame sections.

13. Apparatus as defined in claim 1 wherein said frame comprises a plurality of separate identical frame sections each rotatably supporting one of said crank shaft means, and means releasably connecting said frame sections to define a rigid frame.

14. Apparatus as defined in claim 1 comprising punch and die blocks removably carried by said upper and lower links, respectively.

15. Apparatus as defined in claim 14 wherein each of said upper links includes a link section and a separable punch block section disposed in a recess in the lower surface of said link section, and securing means extending downwardly through said link section and secured to said punch block section.

16. Apparatus as defined in claim 15 wherein said punch block section contains in its lower surface at least one vertical recess, and a downwardly extending punch element the upper end of which is secured in said vertical recess.

17. Apparatus as defined in claim 16 and further including means for adjusting the vertical position of said punch element in said recess.

18. Apparatus as defined in claim 16, wherein said lower links comprise a link section and a removable die section mounted in a recess contained in the upper surface of said link section, said die section containing at least one die opening opposite and corresponding with the punch element, and said link section having a vertical passageway in communication with said die opening.

References Cited by the Examiner UNITED STATES PATENTS 2,394,534 2/1946 Conner 83328 2,406,808 9/1946 Conner 83---328 2,855,998 10/1958 Einhiple 83327 WILLIAM W. DYER, JR., Primary Examiner.

L. TAYLOR, Assistant Examiner. 

1. APPARATUS FOR FORMING A PLURALITY OF TRANSVERSELY SPACED ROWS OF LONGITUDINALLY SPACED APERTURES IN A CONTINUOUS LONGITUDINALLY MOVING WEB OF SHEET MATERIAL, COMPRISING A FRAME HAVING A PLANAR WEB PATH THERETHROUGH, A PLURALITY OF LATERALLY SPACED PUNCH AND DIE MEANS EACH INCLUDING CORRESPONDING UPPER AND LOWER LINKS ARRANGED LONGITUDINALLY OF, PARALLEL WITH, AND ON OPPOSITE SIDES OF SAID WEB PATH, ONE OF SAID LINKS CARRYING AT LEAST ONE PUNCH AND THE CORRESPONDING OTHER OF SAID LINKS CONTAINING AT LEAST ONE DIE OPENING FOR RECEIVING THE PUNCH, MEANS FOR ALTERNATELY DISPLACING SAID LINKS TOWARD AND AWAY FROM EACH OTHER INCLUDING FIRST AND SECOND PAIRS OF PARALLEL CRANK SHAFT MEANS EXTENDING TRANSVERSELY OF SAID WEB PATH ON OPPOSITE SIDES THEREOF, RESPECTIVELY, AND ECCENTRIC CONNECTIONS BETWEEN THE ENDS OF THE LINKS AND THE RESPECTIVE PAIR OF CRANK SHAFT MEANS FOR DISPLACING SAID UPPER AND LOWER LINKS TOWARD AND AWAY FROM EACH OTHER IN ORIENTATIONS PARALLEL WITH SAID WEB PATH TO EFFECT PUNCHING COOPERATION BETWEEN THE PUNCHES AND THE DIE OPENINGS CARRIED THEREBY, SAID ECCENTRIC CONNECTIONS BEING ANGULARLY DISTRIBUTED RELATIVE TO THE AXES OF ROTATION OF SAID CRANK SHAFT MEANS TO CAUSE THE RESULTANT LOAD OF THE LINKS ON EACH OF THE CRANK SHAFT MEANS TO BE BALANCED. 